CN101289964A - Internal combustion engine and combustion method of the same - Google Patents

Internal combustion engine and combustion method of the same Download PDF

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Publication number
CN101289964A
CN101289964A CNA2008100912134A CN200810091213A CN101289964A CN 101289964 A CN101289964 A CN 101289964A CN A2008100912134 A CNA2008100912134 A CN A2008100912134A CN 200810091213 A CN200810091213 A CN 200810091213A CN 101289964 A CN101289964 A CN 101289964A
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China
Prior art keywords
fuel
gaseous fuel
combustion engine
internal
gas
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CNA2008100912134A
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Chinese (zh)
Inventor
野田彻
新城崇
芦田耕一
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Nissan Motor Co Ltd
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Nissan Motor Co Ltd
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Publication of CN101289964A publication Critical patent/CN101289964A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
    • F02B23/08—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition
    • F02B23/10—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition with separate admission of air and fuel into cylinder
    • F02B23/104—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition with separate admission of air and fuel into cylinder the injector being placed on a side position of the cylinder
    • F02B23/105—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition with separate admission of air and fuel into cylinder the injector being placed on a side position of the cylinder the fuel is sprayed directly onto or close to the spark plug
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B17/00—Engines characterised by means for effecting stratification of charge in cylinders
    • F02B17/005—Engines characterised by means for effecting stratification of charge in cylinders having direct injection in the combustion chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
    • F02B23/08—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition
    • F02B23/10—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition with separate admission of air and fuel into cylinder
    • F02B23/101—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition with separate admission of air and fuel into cylinder the injector being placed on or close to the cylinder centre axis, e.g. with mixture formation using spray guided concepts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D15/00—Varying compression ratio
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D19/00—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
    • F02D19/02—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with gaseous fuels
    • F02D19/021—Control of components of the fuel supply system
    • F02D19/023—Control of components of the fuel supply system to adjust the fuel mass or volume flow
    • F02D19/024—Control of components of the fuel supply system to adjust the fuel mass or volume flow by controlling fuel injectors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D19/00—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
    • F02D19/06—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed
    • F02D19/0639—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed characterised by the type of fuels
    • F02D19/0642—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed characterised by the type of fuels at least one fuel being gaseous, the other fuels being gaseous or liquid at standard conditions
    • F02D19/0644—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed characterised by the type of fuels at least one fuel being gaseous, the other fuels being gaseous or liquid at standard conditions the gaseous fuel being hydrogen, ammonia or carbon monoxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D19/00—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
    • F02D19/06—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed
    • F02D19/0663—Details on the fuel supply system, e.g. tanks, valves, pipes, pumps, rails, injectors or mixers
    • F02D19/0668—Treating or cleaning means; Fuel filters
    • F02D19/0671—Means to generate or modify a fuel, e.g. reformers, electrolytic cells or membranes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D19/00—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
    • F02D19/06—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed
    • F02D19/0663—Details on the fuel supply system, e.g. tanks, valves, pipes, pumps, rails, injectors or mixers
    • F02D19/0686—Injectors
    • F02D19/0689—Injectors for in-cylinder direct injection
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D19/00—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
    • F02D19/06—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed
    • F02D19/0663—Details on the fuel supply system, e.g. tanks, valves, pipes, pumps, rails, injectors or mixers
    • F02D19/0686—Injectors
    • F02D19/0692—Arrangement of multiple injectors per combustion chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D19/00—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
    • F02D19/06—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed
    • F02D19/08—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed simultaneously using pluralities of fuels
    • F02D19/081—Adjusting the fuel composition or mixing ratio; Transitioning from one fuel to the other
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/0025—Controlling engines characterised by use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/30—Controlling fuel injection
    • F02D41/3011—Controlling fuel injection according to or using specific or several modes of combustion
    • F02D41/3017—Controlling fuel injection according to or using specific or several modes of combustion characterised by the mode(s) being used
    • F02D41/3035—Controlling fuel injection according to or using specific or several modes of combustion characterised by the mode(s) being used a mode being the premixed charge compression-ignition mode
    • F02D41/3041—Controlling fuel injection according to or using specific or several modes of combustion characterised by the mode(s) being used a mode being the premixed charge compression-ignition mode with means for triggering compression ignition, e.g. spark plug
    • F02D41/3047—Controlling fuel injection according to or using specific or several modes of combustion characterised by the mode(s) being used a mode being the premixed charge compression-ignition mode with means for triggering compression ignition, e.g. spark plug said means being a secondary injection of fuel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/30—Controlling fuel injection
    • F02D41/3094—Controlling fuel injection the fuel injection being effected by at least two different injectors, e.g. one in the intake manifold and one in the cylinder
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F01L1/053—Camshafts overhead type
    • F01L2001/0537—Double overhead camshafts [DOHC]
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
    • F02B23/08—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition
    • F02B23/10—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition with separate admission of air and fuel into cylinder
    • F02B2023/103—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition with separate admission of air and fuel into cylinder the injector having a multi-hole nozzle for generating multiple sprays
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/12—Other methods of operation
    • F02B2075/125—Direct injection in the combustion chamber for spark ignition engines, i.e. not in pre-combustion chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
    • F02B2275/16—Indirect injection
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/0025—Controlling engines characterised by use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
    • F02D41/0027—Controlling engines characterised by use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures the fuel being gaseous
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M25/00—Engine-pertinent apparatus for adding non-fuel substances or small quantities of secondary fuel to combustion-air, main fuel or fuel-air mixture
    • F02M25/10—Engine-pertinent apparatus for adding non-fuel substances or small quantities of secondary fuel to combustion-air, main fuel or fuel-air mixture adding acetylene, non-waterborne hydrogen, non-airborne oxygen, or ozone
    • F02M25/12—Engine-pertinent apparatus for adding non-fuel substances or small quantities of secondary fuel to combustion-air, main fuel or fuel-air mixture adding acetylene, non-waterborne hydrogen, non-airborne oxygen, or ozone the apparatus having means for generating such gases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M27/00—Apparatus for treating combustion-air, fuel, or fuel-air mixture, by catalysts, electric means, magnetism, rays, sound waves, or the like
    • F02M27/02—Apparatus for treating combustion-air, fuel, or fuel-air mixture, by catalysts, electric means, magnetism, rays, sound waves, or the like by catalysts
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/30—Use of alternative fuels, e.g. biofuels

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Combustion Methods Of Internal-Combustion Engines (AREA)
  • Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
  • Electrical Control Of Ignition Timing (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Combined Controls Of Internal Combustion Engines (AREA)

Abstract

An internal combustion engine, including a premixed mixture formation device that forms a premixed mixture of fuel and air in a combustion chamber, a fuel gas supply device that injects fuel gas directly into the combustion chamber, and an ignition device that ignites the fuel gas. The fuel gas supply device is configured to inject the fuel gas into the premixed mixture near a top dead center of a compression stroke such that a spray of the fuel gas passes through a firing position of the ignition device, to produce the spray of the fuel gas in a predetermined area substantially extending from one end of a cylinder bore to the other end as viewed in a cylinder-bore direction defined by a centerline of the cylinder bore.; The ignition device is configured to directly ignite the spray of the fuel gas and to ignite and burn the premixed mixture by way of flame propagation along the spray of the fuel gas.

Description

Internal-combustion engine and combustion method thereof
Technical field
The present invention relates to a kind of internal-combustion engine, light being formed at the fuel in the firing chamber and the premixed gas of air.
Background technique
At present, known spark-ignited internal combustion engine is by improving fuel and Air mixing gas rarefaction the thermal efficiency, reducing the atmospheric pollutant that contains in the exhaust.But rough burning takes place in the spark ignition of weak mixture sometimes.In order to suppress this partial combustion and to enlarge the lean combustion boundary of mixed gas, a lot of technical researches have been carried out.Wherein, especially in recent years, about the technology that makes the premixing compressing ignition of in advance thin mixed gas (thin premixed gas) spontaneous combustion of fuel and air mixing being lighted by Piston Compression has obvious improvement.
As premixing compressing ignition and hydrogen being added the technology that burning is made up, record to some extent in patent documentation 1.In patent documentation 1, in the firing chamber of internal-combustion engine, form the thin premixed gas (first mixed gas) of first fuel and air mixing and compress, and the regional area (spark plug around) of second fuel (hydrogen) in the firing chamber supplied with and second mixed gas of formation stratification, by lighting this second mixed gas the pressure in the firing chamber is risen, make thin premixed gas (first mixed gas) compression autoignition.
Patent documentation 1:(Japan) spy opens the 2004-036538 communique
The internal-combustion engine of record in the patent documentation 1, the mixed gas of first fuel mix becomes the combustion regime of compression autoignition, can not fundamentally solve the essential problem of premixing compressing ignition, promptly can not suppress because of sharply producing the hot combustion noise that causes, avoiding pinking etc.
Summary of the invention
The present invention makes in view of the above problems, and its purpose is to provide a kind of internal-combustion engine, lights thin premixed gas by the many places in the firing chamber, is suppressed at local heat, efficient height and the low emissions of sharply producing.
Internal-combustion engine of the present invention possesses: premixed gas forms mechanism, and it forms the premixed gas of fuel and air in the firing chamber; The gaseous fuel feed mechanism, it is ejected into gaseous direct fuel in the firing chamber; Ignition mechanism, it can light gaseous fuel.In addition, the gaseous fuel feed mechanism is in the spraying of the described gaseous fuel mode by the ignition location of described ignition mechanism, near compression top center, gaseous fuel is ejected in the premixed gas, and on the cylinder diameter direction of firing chamber roughly from the regulation zone that comprises ignition mechanism of the end to end of cylinder diameter, form the spraying of gaseous fuel.In addition, ignition mechanism is directly lighted the spraying of gaseous fuel, makes premixed mixture combustion by flame is propagated along the spraying of gaseous fuel.
According to the present invention, the flame that is caused by the burning of gaseous fuel enlarges along the spraying of gaseous fuel, therefore, can light premixed gas in the many places in the firing chamber.In addition, being sprayed in the firing chamber of gaseous fuel produces strong turbulent flow, promotes flame that the burning by gaseous fuel causes and the mixing of not firing premixed gas, and thin premixed gas is burnt reliably.
Description of drawings
Fig. 1 is the pie graph of the motor (internal-combustion engine) of the 1st mode of execution;
Fig. 2 is the figure of the combustion regime of the thin premixed gas in the firing chamber of in detail expression the 1st mode of execution;
Fig. 3 is the figure of the combustion mode switching of the mixed gas in the firing chamber of expression the 1st mode of execution;
Fig. 4 is the pie graph of the motor (internal-combustion engine) of the 2nd mode of execution;
Fig. 5 is the figure of the combustion regime of the thin premixed gas in the firing chamber of in detail expression the 2nd mode of execution;
Fig. 6 is the figure of the combustion regime of the thin premixed gas in the firing chamber of in detail expression the 2nd mode of execution;
Fig. 7 (a) and (b) are the engine load of the lean combustion operation range (rare pattern (リ one Application)) that is illustrated in the 2nd mode of execution and the graph of a relation of excess air factor or fuel supply ratio;
Fig. 8 is the flow chart of the fuel supply control of expression the 2nd mode of execution;
Fig. 9 is the pie graph of the motor (internal-combustion engine) of the 3rd mode of execution;
Figure 10 is the figure of the combustion regime of the thin premixed gas in the firing chamber of in detail expression the 3rd mode of execution;
Figure 11 is the figure that the compression ratio of the engine load of relative the 3rd mode of execution of expression is set;
Figure 12 is the flow chart of the fuel supply control of expression the 3rd mode of execution.
Embodiment
Below, with reference to the description of drawings embodiments of the present invention.
Fig. 1 is the pie graph of the motor (internal-combustion engine) of the present invention's the 1st mode of execution.
In motor 10, be formed with firing chamber 14 by cylinder head 11, cylinder body 12, piston 13.
Firing chamber 14 can be that suction port 16 is supplied with air inlet from inlet air pathway through suction valve 15, on the other hand, can be that relief opening 18 is discharged with exhaust to exhaust passageway through outlet valve 17.In addition, also has branch pipe part (intake manifold) 19 midway at inlet air pathway.In inlet air pathway, also has throttle valve 20 in the upstream of branch pipe part 19.The action axle of this throttle valve 20 is connected with the output shaft of stepper motor 21, and the output shaft of stepper motor 21 is rotated according to the command signal from control unit of engine described later (ECU) 25 outputs, makes throttle valve 20 actions.
Has the Fuelinjection nozzle 31 that forms mechanism as premixed gas at suction port 16.The liquid fuel F1 that stores in fuel tank 32 supplies with this Fuelinjection nozzle 31 through petrolift 33.This liquid fuel F1 for example is ejected into suction port 16 in exhaust stroke by Fuelinjection nozzle 31, forms the premixed gas of liquid fuel F1 and air in firing chamber 14 at intake stroke.In addition, in the present embodiment, the liquid fuel F1 that stores in fuel tank 32 is made as gasoline, but is not limited thereto.
To have the gaseous fuel feed mechanism be gas spray valve 35 to 14 air inlet side sidepiece in the firing chamber.Be stored in gaseous fuel F2 in the high-pressure gas cylinder 36 through gaseous fuel pump 37 supply gas injection valves 35.The gaseous fuel F2 that is stored in air cylinder 36 is the premixed gas fast fuel of velocity of combustion than formation in the firing chamber 14, in the present embodiment, uses hydrogen, acetylene, ethene etc.Especially, hydrogen is the gaseous fuel of easily lighting, and is adapted at lighting in the spraying.In addition, because hydrogen is compared with premixed gas, velocity of combustion is fast and the lean combustion boundary is also big, does not go out so can keep flame in the spraying of gaseous fuel F2.In addition, also can in gaseous fuel F2, mix oxygen, with this mixed gas supply gas injection valve 35 as oxygenant.
Than the upper central portion of firing chamber 14 more by the side that is provided with of gas spray valve 35, have the ignition mechanism that the spraying of the gaseous fuel F2 that ejects from gas spray valve 35 can be lighted, be spark plug 38.In addition, so long as can in firing chamber 14, light the ignition mechanism of the spraying of gaseous fuel F2, then except that spark plug 38, can also use glow lamp, laser-ignition unit etc.
To based on these signals throttle valve 20, Fuelinjection nozzle 31, gas spray valve 35, spark plug 38 etc. be controlled from the signal input ECU25 of CKP 41, cooling water temperature sensor 42, accelerator pedal sensor 43 etc.
Fig. 2 is the figure that represents the combustion regime of the thin premixed gas in the firing chamber of present embodiment in detail.
Gas spray valve 35 is configured in the air inlet side sidepiece of firing chamber 14, to the sidepiece of the firing chamber 14 of the opposite side of the configuration side of gas spray valve 35 gas jet fuel F2 flatly.In addition, the ignition location of spark plug 38 (ignition gap) is arranged in the spraying of the gaseous fuel F2 that is ejected by gas spray valve 35, and is positioned at the configuration side of more leaning on gas spray valve 35 than the spray orifice of gas spray valve 35 and the centre of the final point of arrival of the spraying of gaseous fuel F2 (sidepiece of the firing chamber 14 of the opposite side of configuration side of gas spray valve 35).
End (near the compression top center) in compression stroke, gaseous fuel F2 is ejected in the thin premixed gas of the liquid fuel F1 that is pre-formed in firing chamber 14 and air from gas spray valve 35.On the cylinder diameter direction of firing chamber,, form the spraying of gaseous fuel roughly from the regulation zone that comprises ignition mechanism of the end to end of cylinder diameter.The front end of the spraying of the gaseous fuel F2 that ejects by ignition location (ignition gap) back of spark plug 38 and during gas spray valve 35 burner oil F2 in the middle of constantly after, spark plug 38 is lighted the spraying of gaseous fuel F2.The flame that is produced by this spark ignition is along the mobile expansion of the spraying of gaseous fuel F2.At this moment, because the turbulent flow of gaseous fuel F2 in spraying is reinforced, flame promptly enlarges down to the front end of the spraying of gaseous fuel F2.And the jet flow flame that is diffused into the gaseous fuel F2 in the firing chamber 14 makes the thin premixed mixture combustion that is pre-formed in firing chamber 14 by flame propagation, and promotes the burning of weak mixture by turbulent mixture.
In addition, in the present embodiment, can and control the period of combustion of the gaseous fuel F2 in the firing chamber 14 according to the fuel injection time (fuel injection beginning time, fuel injection end time) of gas spray valve 35 firing time of spark plug 38.In addition, can come control gaseous fuel F2 to produce the time of ignition heat according to the fuel injection amount of gas spray valve 35.Therefore, also consider key elements such as the thermal efficiency, effulent, noise, vibration, set the fuel injection time of gas spray valve 35 and the firing time of fuel injection amount and spark plug 38, be stored in these setting values among the ECU25 in advance, by with reference to the fuel injection time of the above-mentioned setting value control gaseous injection valve 35 corresponding and the firing time of fuel injection amount and spark plug 38 with the operating condition (engine load, internal-combustion engine rotational speed etc.) of motor 10, hot generation time and speed in the time of can suitably controlling thin premixed mixture combustion.
Fig. 3 is the combustion mode switching figure of mixed gas in the firing chamber of expression present embodiment.
In the present embodiment, under motor 10 low-loads and slow-revving situation, form the lean combustion operation range, as mentioned above, utilize gaseous fuel F2 to light thin premixed gas.Thus, can realize the raising of the thermal efficiency and the reduction of effulent.In addition, under motor 10 high loaies or high-revolving situation, form dense burning operation range (ス ト イ キ Ran Ware ?Rotating Collar territory), only liquid fuel F1 and Air mixing gas are supplied with in firing chamber 14, and this mixed gas is directly carried out spark ignition and carries out dense burning (ス ト イ キ fires baked).Thus, can realize the raising of exporting.
According to present embodiment, the spraying of gaseous fuel F2 is spread in firing chamber 14 by the ignition location of ignition mechanism (spark plug 38), therefore, being sprayed at of gaseous fuel F2 produces strong turbulent flow in the firing chamber 14, promote flame and the not mixing of the thin premixed gas of combustion that gaseous fuel F2 burning produces, so can make the lean mixture gas firing reliably.
According to present embodiment, the flame that gaseous fuel F2 burning produces enlarges along the spraying of gaseous fuel F2, therefore, can light thin premixed gas in the many places in the firing chamber 14.
In addition, according to present embodiment, gaseous fuel F2 is ejected under vaporized state in the firing chamber 14, therefore, and in the time of can avoiding being directly injected to liquid fuel in the firing chamber 14, because of not enough sooting and the cigarette that produces at ignition mechanism (spark plug 38) of the gasification of liquid fuel.
According to present embodiment, the ignition location of ignition mechanism (spark plug 38) is positioned at the configuration side of more leaning on gaseous fuel feed mechanism (gas spray valve 35) than the centre of the final point of arrival of the spraying of the spray orifice of gaseous fuel feed mechanism (gas spray valve 35) and gaseous fuel F2, therefore, the spraying that can guarantee the gaseous fuel F2 that ejects from gaseous fuel feed mechanism (gas spray valve 35) is dispersed to the space in ignition location downstream side, also can apply flexibly the turbulent invigoration effect that the spraying of gaseous fuel F2 causes effectively in the downstream side of ignition location, so can light thin premixed gas in many places.
In addition, according to present embodiment, ignition mechanism (spark plug 38) the front end of gaseous fuel F2 spraying by behind the ignition location of ignition mechanism (spark plug 38) and in the middle of gaseous fuel feed mechanism (gas spray valve 35) gas jet fuel F2 period constantly after, light the spraying of gaseous fuel F2, so spraying of 14 internal cause gaseous fuel F2 in the firing chamber and after forming enough field of turbulent flows, light the spraying of gaseous fuel F2, therefore, the diffusion of flame can be promoted, and thin premixed mixture combustion can be made more reliably along the spraying of gaseous fuel F2.
According to present embodiment, gaseous fuel feed mechanism (gas spray valve 35) is configured in the sidepiece of firing chamber 14, dispose the sidepiece gas jet fuel F2 of the firing chamber 14 of the opposite side of side towards gaseous fuel feed mechanism (gas spray valve 35), therefore, compare with the situation that gaseous fuel feed mechanism (gas spray valve 35) is configured in the upper central portion of firing chamber 14, gaseous fuel feed mechanism (gas spray valve 35) can be set easily.
In addition, according to present embodiment, gaseous fuel F2 is the velocity of combustion gaseous fuel faster than premixed gas (hydrogen, acetylene, ethene etc.), therefore, can light gaseous fuel F2 reliably in the jet flow of gaseous fuel F2 by ignition mechanism (spark plug 38).In addition, light the flame that produces because of this and promptly enlarge,, can realize the expansion of lean combustion boundary so can suppress the partial combustion of thin premixed gas along the spraying of gaseous fuel F2 owing to can make.
According to present embodiment, gaseous fuel F2 is for containing the mixed gas of oxygenant (oxygen etc.), when propellant composition is the overrich state in the spraying of gaseous fuel F2 thus, can suppress the rough burning that causes because of hypoxia, and can promote flame along the spraying of gaseous fuel F2 and enlarge.
Below, the 2nd mode of execution of the present invention is described.
Fig. 4 is the pie graph of the motor (internal-combustion engine) of the present invention's the 2nd mode of execution.
Difference with the 1st mode of execution shown in Figure 1 is described.
Among Fig. 4, suction port 16 has the first Fuelinjection nozzle 51a and the second Fuelinjection nozzle 51b that forms mechanism as premixed gas.The hydrocarbon fuel F3 that pyrophorisity is low supplies with to the first Fuelinjection nozzle 51a from fuel segregating unit 61 described later through petrolift 62.The hydrocarbon fuel F4 that pyrophorisity is high supplies with to the second Fuelinjection nozzle 51b from fuel reforming device 63 described later through petrolift 64.In addition, the hydrocarbon fuel F3 that so-called pyrophorisity is low is for being rich in hydrocarbon fuels such as aromatic hydrocarbon, isoalkane, alkene; The high hydrocarbon fuel F4 of so-called pyrophorisity is the hydrocarbon fuel that is rich in normal alkane etc.
14 the upper central portion in the firing chamber as the gaseous fuel feed mechanism, has the gas spray valve 35 of the 14 female cone shape ground gas jet fuel F5 in the firing chamber.Gaseous fuel F5 through gaseous fuel pump 65 from fuel reforming device 63 supply gas injection valves 35 described later.
In addition, on firing chamber 14, more lean on the side that is provided with of gas spray valve 35 in the spray orifice of the gas spray valve 35 that is provided with than the upper central portion of firing chamber 14 and the centre of the sidepiece (the final point of arrival of the spraying of gaseous fuel F5) of firing chamber 14, have the spark plug 38 of the spraying that can light the gaseous fuel F5 that ejects by gas spray valve 35.
Supplying with the hydrocarbon fuel that comes from the outside carries to fuel segregating unit 61 from the fuel tank 32 that stores this fuel through low-pressure fuel pump 66.In fuel segregating unit 61, the normal alkane in the fuel is separated by the diffusion barrier in the fuel segregating unit 61, and carries to fuel reforming device 63 through petrolift (not shown).In addition, fuel reforming device 63 becomes the structure of the exhaust heat that can accept motor 10.Part by fuel segregating unit 61 isolated normal alkanes is transformed into hydrogen (gaseous fuel F5) and the low hydrocarbon fuel F3 of pyrophorisity by the dehydrogenation reaction (modified-reaction) of utilizing catalyzer (platinum series catalysts etc.) in fuel reforming device 63.As this reaction example, with normal alkane (C 7H 16) when carrying out fuel reforming by the dehydrocyclization reaction, be following chemical equation by fuel reforming device 63.
C 7H 16(normal alkane) → C 7H 8(toluene)+4H 2
In addition, the dehydrocyclization reaction is heat absorption reaction.
Supply with to gas spray valve 35 by gaseous fuel pump 65 by the hydrogen (gaseous fuel F5) that fuel reforming mechanism 63 generates.The low hydrocarbon fuel F3 of pyrophorisity that is generated by fuel reforming device 63 returns fuel segregating unit 61 through petrolift (not shown), with separate normal alkane by the diffusion barrier in the fuel segregating unit 61 after residual fraction together, as the low hydrocarbon fuel F3 of pyrophorisity, supply with to the first Fuelinjection nozzle 51a through petrolift 62.In addition, in fuel reforming device 63, the normal alkane of not supplying with modified-reaction is supplied with to the second Fuelinjection nozzle 51b through petrolift 64 as the high hydrocarbon fuel F4 of pyrophorisity.
In the present embodiment, the part by fuel segregating unit 61 isolated normal alkanes also can generate hydrogen (gaseous fuel F5) by the partial oxidation reaction (modified-reaction) that utilizes catalyzer (rhodium series catalysts etc.) at fuel reforming device 63.As this reaction example, with normal alkane (C 7H 16) when carrying out fuel reforming by partial oxidation reaction, be following chemical equation by fuel reforming device 63.
C 7H 16(normal alkane)+3.5O 2→ 7C O+8H 2
In addition, partial oxidation reaction is an exothermic reaction.
Supply with to gas spray valve 35 by gaseous fuel pump 65 by the hydrogen (gaseous fuel F5) that fuel reforming device 63 generates.In addition, in fuel reforming device 63, the normal alkane of not supplying with modified-reaction is supplied with to the second Fuelinjection nozzle 51b through petrolift 64 as the high hydrocarbon fuel F4 of pyrophorisity.
Fig. 5 is the figure that represents the thin premixed gas state in the firing chamber of present embodiment in detail.
Gas spray valve 35 is configured in the upper central portion of firing chamber 14, the 14 female cone shapes gas jet fuel F5 (hollow cone shape) in the firing chamber.In addition, spark plug 38 is configured to: its ignition location (ignition gap) be arranged in the spraying of the gaseous fuel F5 that ejects by gas spray valve 35 and than the centre of the final point of arrival (sidepiece of firing chamber 14) of the spraying of the spray orifice of gas spray valve 35 and gaseous fuel F5 more by the configuration side of gas spray valve 35.
By high hydrocarbon fuel F4 and the air of pyrophorisity low hydrocarbon fuel F3, pyrophorisity, in the weak mixture that in firing chamber 14, forms in advance, at compression stroke terminal point (near the compression top center), from gas spray valve 35 gas jet fuel F5.On the cylinder diameter direction of firing chamber,, form the spraying of gaseous fuel from the regulation zone that contains ignition mechanism of the end to end of cylinder diameter.The front end of the spraying of the gaseous fuel F5 that ejects by spark plug 38 ignition location (ignition gap) back and gas spray valve 35 gas jet fuel F5 during in the middle of constantly after, spark plug 38 is lighted the spraying of gaseous fuel F5.The flame that is produced by this spark ignition enlarges along the flowing of spraying of gaseous fuel F5.At this moment, interior turbulent flow is reinforced because gaseous fuel F5 sprays, so flame promptly enlarges down to the front end of gaseous fuel F5 spraying.And the jet flow flame of the gaseous fuel F5 that diffusion is come in firing chamber 14 makes the thin premixed mixture combustion that forms in advance by flame propagation in firing chamber 14, and promotes the burning of thin premixed gas by turbulent mixture.In addition, owing to have the high hydrocarbon fuel F4 of pyrophorisity, so can in firing chamber 14, bring out spontaneous combustion partly.Therefore, in the wide range in firing chamber 14, weak mixture is burnt well.
In addition, in the present embodiment, except the combustion regime of thin premixed gas shown in Figure 5, also can utilize the combustion regime of thin premixed gas shown in Figure 6.
Among Fig. 6, gas spray valve 35 is single spray orifice, towards the central part gas jet fuel F5 of the end face of piston 13.In addition, the groove 13a that has concavity at the end face central part of piston 13.The spraying of the gaseous fuel F5 that ejects from gas spray valve 35 collides groove 13a and along the bottom surface diffusion of groove 13a, rolls to firing chamber 14 sides along the peripheral wall surfaces of groove 13a.In addition, spark plug 38 is configured to: its ignition location (ignition gap) be arranged in the spraying of the gaseous fuel F5 that ejects by gas spray valve 35 and than the centre of the final point of arrival (bottom surface of the groove 13a of compression top center) of the spray orifice of gas spray valve 35 and gaseous fuel F5 spraying more by the configuration side of gas spray valve 35.
Fig. 7 is the figure of the relation of the engine load of the lean combustion operation range (rare pattern (リ one Application)) that is illustrated in present embodiment and excess air factor or fuel supply ratio.
The engine load of Fig. 7 (a) expression lean combustion operation range (rare pattern) and the relation of excess air factor.
The fuel supply control mechanism that ECU25 possessed is controlled throttle valve 20, the first Fuelinjection nozzle 51a, the second Fuelinjection nozzle 51b and gas spray valve 35, with the reduction along with engine load, excess air factor is increased.Thus, engine load reduces more, and the premixed gas that is formed in the firing chamber 14 is got over rarefaction.
The engine load of Fig. 7 (b) expression lean combustion operation range (rare pattern) and the relation of fuel supply ratio.
The pre-mixed fuel that ECU25 possessed is supplied with control mechanism the first Fuelinjection nozzle 51a and the second Fuelinjection nozzle 51b is controlled, with reduction along with engine load, the fuel supply ratio of the low hydrocarbon fuel F3 of pyrophorisity is reduced, and the fuel supply ratio of the high hydrocarbon fuel F4 of pyrophorisity is increased.Thus, along with the reduction of engine load, the pyrophorisity that is formed at the premixed gas in the firing chamber 14 increases.
In addition, the fuel supply control mechanism that ECU25 possessed is controlled gas spray valve 35, with the reduction along with engine load, the fuel supply ratio of gaseous fuel F5 is increased.Thus,, strengthen the spraying flame that gaseous fuel F5 causes, can improve the burning facilitation effect of premixed gas, premixed gas is burnt reliably along with the reduction of engine load.
Fig. 8 is the flow chart of the fuel supply control of expression present embodiment.
ECU25 reads the signal of being exported by various sensors such as CKP 41, cooling water temperature sensor 42, accelerator pedal sensor 43 at step S102, judges operating conditions such as engine load, internal-combustion engine rotational speed at step S103.Based on this judged result, utilize above-mentioned Fig. 3 to judge the combustion mode of the mixed gas in the firing chamber 14 at step S104.Particularly, if the low-load and the slow-speed of revolution then form unthickened fuel operation range (rare pattern); If high load or high rotating speed then form dense burning operation range (dense pattern (ス ト イ キ)).
When being judged to be " rare pattern " at step S104, enter step S105, with reference to " rare pattern is sprayed table with (リ one Application is used) F3 " that be stored in advance among the ECU25, the fuel injection timing of the Fuelinjection nozzle 51a of the hydrocarbon fuel F3 that decision injection pyrophorisity is low and fuel injection amount etc.Then, enter step S106, with reference to " rare pattern is sprayed table with F4 " that be stored in advance among the ECU25, the fuel injection timing of the Fuelinjection nozzle 51b of the hydrocarbon fuel F4 that decision injection pyrophorisity is high and fuel injection amount etc.Then, enter step S107, with reference to " rare pattern is sprayed table with F5 " that be stored in advance among the ECU25, the gaseous fuel injection timing of the gas spray valve 35 of decision gas jet fuel F5 and gaseous fuel emitted dose etc. enter step S110.In step S110, based on determination result by step S105, step S106 and step S107, by fuel supply control mechanism and the premixed gas fuel supply control mechanism that has among the ECU25, the supply period and the delivery volume of the various fuel of control supply engine 10.
When being judged to be " dense pattern " at step S104, enter step S115, with reference to " dense pattern is sprayed table with (ス ト イ キ uses) F3 " that be stored in advance among the ECU25, fuel injection timing and the fuel injection amount of the Fuelinjection nozzle 51a of the low hydrocarbon fuel F3 of pyrophorisity sprayed in decision.Thereafter, enter step S110, based on the determination result of step S115, by fuel supply control mechanism and the premixed gas fuel supply control mechanism that has among the ECU25, the supply period and the delivery volume of the fuel of control supply engine 10 (the just low hydrocarbon fuel F3 of pyrophorisity).
Especially, according to present embodiment, gaseous fuel feed mechanism (gas spray valve 35) is configured in the top central part of firing chamber 14, the 14 female cone shape ground gas jet fuel F5 in the firing chamber, therefore the spraying of gaseous fuel F5 can be spread on non-migration ground in firing chamber 14, so can be suppressed at the local unburned hydrocarbons that produce in the firing chamber 14.
In addition, according to present embodiment, gaseous fuel feed mechanism (gas spray valve 35) is single spray orifice, be configured in the top central part of firing chamber 14, groove 13a gas jet fuel F5 towards the end face of piston 13, therefore compare with the situation of the 14 female cone shape ground gas jet fuel F5 in the firing chamber, can use to constitute simple gaseous fuel feed mechanism (gas spray valve 35), so can be suppressed at the local unburned hydrocarbon that produces in the firing chamber 14 easilier.
In addition, according to present embodiment, the gaseous fuel of gaseous fuel F5 for will when the outside hydrocarbon fuel of supplying with carries out fuel reforming, generating by modified-reaction, therefore, the fuel that can supply with from the outside makes a kind of.In addition, owing to need not to be provided in addition the high-pressure gas cylinder etc. of stored gas fuel F5,, can make the fuel supply system miniaturization so compare with situation with this high-pressure gas cylinder.
According to present embodiment, owing to generate the exhaust heat that the modified-reaction of gaseous fuel F5 utilizes internal-combustion engine (motor 10), therefore, can suppress the energy loss that causes because of exhaust heat, thereby can improve the thermal efficiency.
According to present embodiment, be dehydrogenation reaction owing to generate the modified-reaction of gaseous fuel F5, so compare, can access the high hydrogen of purity with partial oxidation reaction.Therefore, compare, can reduce the fuel injection amount that sprays from gaseous fuel feed mechanism (gas spray valve 35), so can make the fuel supply system miniaturization with the situation of partial oxidation reaction.
In addition, according to present embodiment, the modified-reaction that generates gaseous fuel F5 is partial oxidation reaction (exothermic reaction), compares with the situation of dehydrogenation reaction (heat absorption reaction), can reduce the heat of supplying with when carrying out modified-reaction.
According to present embodiment, because forming mechanism to premixed gas, hydrocarbon fuel F3 that pyrophorisity is low supplies with, so can suppress the generation of the pinking that causes because of rapid burning etc.
In addition, according to present embodiment, because the hydrocarbon fuel F4 that pyrophorisity is high forms mechanism to premixed gas and supplies with, so when the very thin low-load of premixed gas, except the spraying by gaseous fuel F5 promotes the effect of combustion, can also obtain the spontaneous combustion of premixed gas and promote effect of combustion, enlarge the lean combustion boundary.
In addition, according to present embodiment, in ECU25, has the fuel supply control mechanism, it is controlled as follows, promptly, reduction along with internal-combustion engine (motor 10) load, make and form mechanism by premixed gas and be formed at premixed gas rarefaction in the firing chamber 14, and the delivery volume by gaseous fuel feed mechanism (gas spray valve 35) gas supplied fuel F5 in firing chamber 14 is increased, therefore, when low-load, thin relatively premixed gas, spraying that can enlargement gas fuel F5 promotes effect of combustion, can suppress the rough burning of thin premixed gas.In addition, when high load, at premixed gas is under the situation of overrich state (dense), because the delivery volume of gaseous fuel F5 is reduced, so can reduce the spraying of gaseous fuel F5 promotes effect of combustion, does not make hot generation speed excessive and control, as a result, can suppress the generation of noise and vibration etc.
According to present embodiment, form the fuel that uses in the mechanism at premixed gas and be pyrophorisity high hydrocarbon fuel F4 and the low hydrocarbon fuel F3 of pyrophorisity, in ECU25, has premixed gas fuel supply control mechanism, it is controlled as follows, promptly, reduction along with internal-combustion engine (motor 10) load, the supply ratio of the high hydrocarbon fuel F4 of pyrophorisity is increased, and the supply ratio of the low hydrocarbon fuel F3 of pyrophorisity is reduced, therefore, when low-load, can enlarge the lean combustion boundary, when high load, can suppress the generation of pinking.
In addition, according to present embodiment, the fuel of hydrocarbon fuel F3 that pyrophorisity is low for by modified-reaction the hydrocarbon fuel that is come by the outside supply being carried out generating behind the fuel reforming, therefore need not to be provided in addition to store the fuel tank of hydrocarbon fuel F3 etc., so compare with the situation that possesses this fuel tank, can make the fuel supply system miniaturization.
According to present embodiment, the modified-reaction that generates the low hydrocarbon fuel F3 of pyrophorisity is the dehydrocyclization reaction, therefore can generate the low fuel of pyrophorisity that is rich in aromatic hydrocarbon, and can generate hydrogen (gaseous fuel F5).
In addition, according to present embodiment, the hydrocarbon fuel F4 that pyrophorisity is high supplies with the fuel that obtains behind the next hydrocarbon fuel for separating from the outside by diffusion barrier, therefore, need not to be provided in addition fuel tank that stores hydrocarbon fuel F4 etc., so compare with the situation that possesses this fuel tank, can make the fuel supply system miniaturization.
Then, the 3rd mode of execution of the present invention is described.
Fig. 9 is the pie graph of the motor (internal-combustion engine) of the present invention's the 3rd mode of execution.
Difference with the 2nd mode of execution shown in Figure 4 is described.
Among Fig. 9,14 the upper central portion in the firing chamber as the gaseous fuel feed mechanism, is provided with the first gas spray valve 55a and the second gas spray valve 55b.The first gas spray valve 55a is single spray orifice, towards the central part gas jet fuel F5 of piston 13 end faces.Groove (little bowl) 13b that has concavity at the central part of the end face of piston 13.In addition, second gas spray valve 55b gas jet fuel F5 radially in firing chamber 14.In the present embodiment, through gaseous fuel pump 65 gaseous fuel F5 is supplied with to the first gas spray valve 55a and the second gas spray valve 55b from fuel reforming mechanism 63, but, the first gas spray valve 55a and the second gas spray valve 55b are independent separately, can control fuel supply by the fuel supply control mechanism that has among the ECU25.
Figure 10 is the figure that represents the burning form of the thin premixed gas in the firing chamber of present embodiment in detail.
In the high hydrocarbon fuel F4 of hydrocarbon fuel F3, the pyrophorisity low by pyrophorisity and air are pre-formed thin premixed gas in firing chamber 14, end (compression top center near) groove (little bowl) the 13b gas jet fuel F5 of the concavity that possesses towards end face central part from the first gas spray valve 55a at piston 13 in compression stroke.Thus, form the mixed air mass that mixes of the spraying of thin premixed gas and gaseous fuel F5 between the first gas spray valve 55a in firing chamber 14 and groove (little bowl) 13b.Then, from second gas spray valve 55b gas jet fuel F5 in firing chamber 14 radially.At this moment, the spraying of radial gaseous fuel F5 runs through the mixing air mass and forms.In addition, spark plug 38 is configured to: its ignition location (ignition gap) is arranged in and mixes air mass and more lean on the configuration side of gas spray valve 55a than the spray orifice of gas spray valve 55a and the centre of the final point of arrival that mixes air mass (bottom surface of the groove of compression top center (little bowl) 13b), lights the mixing air mass.This is lighted the flame that causes and also enlarges in the spraying of the gaseous fuel F5 of radial formation, and the wide range in firing chamber 14 forms the spraying flame of gaseous fuel F5.
Figure 11 is the figure that the compression ratio of the engine load of the relative present embodiment of expression is set.
In the present embodiment, have the variable compression ratio (not shown) of the compression ratio that can change motor 10, in ECU25, have the compression ratio control mechanism (not shown) that uses this variable compression ratio, controls compression ratio according to engine load.This compression ratio control mechanism is controlled compression ratio based on the setting value of the compression ratio of relative engine load shown in Figure 11 relatively.When motor 10 is low-load, in order to improve the thermal efficiency, improve compression ratio, otherwise, during for high load,, reduce compression ratio for fear of abnormal combustions such as pinkings.
Figure 12 is the flow chart of the fuel supply control of expression present embodiment.
Difference with the 2nd mode of execution shown in Figure 8 is described.
At first, in the step S107 of Fig. 8, with reference to " rare pattern is sprayed table with F5 " that be stored in advance among the ECU25, the fuel injection timing of the gas spray valve 35 of decision gas jet fuel F5 and fuel injection amount etc., and in the step S107 of Figure 12, with reference to " rare pattern is sprayed table with F5 " that be stored in advance among the ECU25, the first gas spray valve 55a of decision gas jet fuel F5 and the fuel injection timing of the second gas spray valve 55b and fuel injection amount etc., above aspect is different.
In addition, in Figure 12, before step S110 carries out fuel supply control, read in the compression ratio chart by step S208, S209 controls compression ratio by step, and this point is different with Fig. 8.
In step S208, based on the operating condition that step S103 judges, read in compression ratio chart (Figure 11), enter step S209.
In step S209, behind compression ratio control mechanism control compression ratio, enter step S110, carry out the fuel supply control identical with Fig. 8.
Especially, according to present embodiment, the gaseous fuel feed mechanism is made of the first gas spray valve 55a and the second gas spray valve 55b of the top central part that is disposed at firing chamber 14, first gas spray valve is towards groove (little bowl) the 13b gas jet fuel F5 of piston-top surface, after forming with the mixed mixing air mass of the spraying of premixed gas and gaseous fuel F5, second gas spray valve gas jet fuel F5 radially in firing chamber 14, form the spraying of radial gaseous fuel F5, light the mixing air mass by ignition mechanism (spark plug 38), the spraying of the radial gaseous fuel F5 of flame ignition that forms by this burning, therefore, the spraying of gaseous fuel F5 can be spread on non-migration ground in firing chamber 14, and can be suppressed at the local unburned hydrocarbon that produces in the firing chamber 14.
In addition, in the present invention, be not limited in integral combustion chamber 14 premixed gas that forms, even, also can be suitable for the present invention for the premixed gas (that is, the stratification mixed gas) of the formation of the part firing chamber 14 in.
The present application advocates that the Japanese patent application No. spy who proposed on April 20th, 2007 is willing to the preference of 2007-111085, here cites its content.

Claims (21)

1, a kind of internal-combustion engine is characterized in that, comprising:
Premixed gas forms mechanism, and this premixed gas forms mechanism forms fuel and air in the firing chamber premixed gas;
The gaseous fuel feed mechanism, this gaseous fuel feed mechanism is ejected into gaseous direct fuel in the described firing chamber;
Ignition mechanism, this ignition mechanism be in order to lighting described gaseous fuel,
Described gaseous fuel feed mechanism with the spraying of described gaseous fuel by the mode of the ignition location of described ignition mechanism, near compression top center, described gaseous fuel is ejected in the described premixed gas, and on the cylinder diameter direction of firing chamber roughly from the regulation zone that comprises ignition mechanism of the end to end of cylinder diameter, form the spraying of gaseous fuel
Described ignition mechanism is directly lighted the spraying of described gaseous fuel, lights described premixed gas by flame is propagated along the spraying of described gaseous fuel.
2, internal-combustion engine as claimed in claim 1, it is characterized in that described ignition mechanism is configured to: the ignition location of described ignition mechanism than the neutral position of the final point of arrival of the spraying of the spray orifice of described gaseous fuel feed mechanism and described gaseous fuel more by the spray orifice side of described gaseous fuel feed mechanism.
3, internal-combustion engine as claimed in claim 1 or 2, it is characterized in that, in the middle of after the front end of described gaseous fuel spraying is by the ignition location of described ignition mechanism and during described gaseous fuel feed mechanism sprays described gaseous fuel constantly after, described ignition mechanism is lighted described spraying.
4, internal-combustion engine as claimed in claim 1 or 2, it is characterized in that, described gaseous fuel feed mechanism is the gas spray valve that is disposed at the sidepiece of described firing chamber, and this gas spray valve sprays described gaseous fuel towards the described firing chamber sidepiece with the opposite side of its configuration side.
5, internal-combustion engine as claimed in claim 1 or 2 is characterized in that, described gaseous fuel feed mechanism is the gas spray valve that is disposed at the top central part of described firing chamber, and this gas spray valve is in described firing chamber and sprays described gaseous fuel coniformly.
6, internal-combustion engine as claimed in claim 1 or 2 is characterized in that, described gaseous fuel feed mechanism is the gas spray valve that is disposed at the top central part of described firing chamber, and this gas spray valve sprays described gaseous fuel towards the groove of piston-top surface.
7, internal-combustion engine as claimed in claim 1 or 2, it is characterized in that, described gaseous fuel feed mechanism is made of first gas spray valve and second gas spray valve of the top central part that is disposed at described firing chamber, described first gas spray valve sprays described gaseous fuel towards the groove of piston-top surface, behind the mixing air mass that the spraying that forms described premixed gas and described gaseous fuel mixes mutually, described second gas spray valve is in described firing chamber and sprays described gaseous fuel radially and form radial spraying, utilize described ignition mechanism to light described mixing air mass, by the described radial spraying of flame ignition of this burning generation.
8, internal-combustion engine as claimed in claim 1 or 2 is characterized in that, the velocity of combustion of described gaseous fuel is faster than the velocity of combustion of described premixed gas.
9, internal-combustion engine as claimed in claim 1 or 2 is characterized in that, described gaseous fuel is the hydrocarbon fuel of being supplied with by the outside to be carried out the gaseous fuel that generates behind the fuel reforming by modified-reaction.
10, internal-combustion engine as claimed in claim 9 is characterized in that, the described modified-reaction that generates described gaseous fuel utilizes the exhaust gas heat of described internal-combustion engine.
11, internal-combustion engine as claimed in claim 9 is characterized in that, the described modified-reaction that generates described gaseous fuel is a dehydrogenation reaction.
12, internal-combustion engine as claimed in claim 9 is characterized in that, the described modified-reaction that generates described gaseous fuel is a partial oxidation reaction.
13, internal-combustion engine as claimed in claim 1 or 2 is characterized in that, described gaseous fuel is a hydrogen.
14, internal-combustion engine as claimed in claim 1 or 2 is characterized in that, described gaseous fuel is the mixed gas that contains oxygenant.
15, internal-combustion engine as claimed in claim 1 or 2, it is characterized in that having the fuel supply control mechanism, this fuel supply control mechanism is controlled as follows: along with the reduction of engine load, with described premixed gas rarefaction, and the supply ratio of described gaseous fuel is increased.
16, internal-combustion engine as claimed in claim 1 or 2, it is characterized in that, the fuel that forms mechanism's supply to described premixed gas is high hydrocarbon fuel of pyrophorisity and the low hydrocarbon fuel of pyrophorisity, described internal-combustion engine has premixed gas fuel supply control mechanism, this premixed gas fuel supply control mechanism is controlled as follows: along with the reduction of engine load, the supply ratio of the high hydrocarbon fuel of described pyrophorisity is increased, and the supply ratio of the low hydrocarbon fuel of described pyrophorisity is reduced.
17, internal-combustion engine as claimed in claim 16 is characterized in that, the hydrocarbon fuel that described pyrophorisity is low is the hydrocarbon fuel of being supplied with by the outside to be carried out the fuel that generates behind the fuel reforming by modified-reaction.
18, internal-combustion engine as claimed in claim 17 is characterized in that, the described modified-reaction that generates the low hydrocarbon fuel of described pyrophorisity utilizes the exhaust gas heat of described internal-combustion engine.
19, internal-combustion engine as claimed in claim 17 is characterized in that, the described modified-reaction that generates the low hydrocarbon fuel of described pyrophorisity is the dehydrocyclization reaction.
20, internal-combustion engine as claimed in claim 16 is characterized in that, the hydrocarbon fuel that described pyrophorisity is high is the fuel that will obtain after will being separated by the hydrocarbon fuel that the outside is supplied with by diffusion barrier.
21, a kind of combustion method of internal-combustion engine is characterized in that, may further comprise the steps:
In the firing chamber, form premixed gas;
Near compression top center time, on the cylinder diameter direction of firing chamber,, form the gaseous fuel layer roughly from the regulation zone of containing ignition mechanism of the end to end of cylinder diameter;
Light described gaseous fuel layer.
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